Sealing device

ABSTRACT

A sealing device provides sealing so as to prevent a sealed fluid in a machine inner side from leaking to a machine outer side between a housing and a rotating shaft which is inserted to a shaft hole provided in the housing. The sealing device has a seal flange which is installed to an outer periphery of the rotating shaft, and a seal lip which is installed to an inner periphery of the shaft hole of the housing and slidably comes into contact with the seal flange over an entire periphery. The sealing device includes a thread groove which exerts a fluid pumping action when the rotating shaft rotates. The thread groove is provided at a position which does not intersect a contact area where the seal lip slidably comes into contact with the seal flange over the entire periphery, thereby suppressing generation of static leakage.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a Divisional Patent Application of U.S. applicationSer. No. 15/317,718, filed on Dec. 9, 2016, which is a U.S. NationalStage Application of International Application No. PCT/JP2015/066541,filed on Jun. 9, 2015 and claims priority to Japanese Application Nos.2014-119271, filed on Jun. 10, 2014, 2014-119273, filed on Jun. 10,2014, 2014-119275, filed on Jun. 10, 2014 and 2014-140118, filed on Jul.8, 2014. The entire disclosures of the above applications areincorporated herein by reference.

BACKGROUND OF THE INVENTION Field of the Invention

The present invention relates to a sealing device which prevents a fluidto be sealed in an inside of a machine from leaking out to an outside ofa machine in a motor vehicle, a general machine and an industrialmachine, and is provided with a structure in which a non-rotating seallip is brought into slidable contact with a seal flange in a rotatingside. The sealing device according to the present invention is used, forexample, as a rotating oil seal which seals an oil in an inside of amachine in a field associated to the motor vehicle.

Description of the Conventional Art

As shown in FIGS. 13A and 13B, there has been conventionally known asealing device 101 which seals so as to prevent a sealed fluid (oil) ina machine inner side A leaking out to a machine outer side B between ahousing 51 and a rotating shaft 61 passing through a shaft hole 52provided in the housing 51, the sealing device 101 being constructed bya combination of a slinger 111 which is installed to an outer peripheryof a rotating shaft 61, and a lip seal member 121 which is installed toan inner periphery of the shaft hole 52 in the housing 51.

The slinger 111 is made of a rigid material such as a metal, integrallyhas a sleeve portion 112 which is fixed to an outer peripheral surfaceof the rotating shaft 61, and a flange portion 113 which is provided inone end of the sleeve portion 112, and is provided in a machine outerside end face 113 a of the flange portion 113 with a thread groove 114exerting a fluid pumping action caused by a centrifugal force when therotating shaft 61 rotates.

On the other hand, the lip seal member 121 has an attachment ring 122which is fixed to an inner peripheral surface of the shaft hole 52 inthe housing 51, and a rubber-like elastic body 123 which is fitted tothe attachment ring 122, and is provided with a seal lip (an end facelip) 124 which slidably comes into close contact with the machine outerside end face 113 a of the flange portion 113 in the slinger 111, by therubber-like elastic body 123.

In recent years, a development of fuel efficient cars has beenaccelerated in a motor vehicle industry due to an environmental problem,and torque reduction at a time of rotating is listed up as needs for anoil seal for an engine. Under such a condition, according to the sealingdevice 101 having the end face lip structure shown in FIG. 13, the lowtorque can be achieved in comparison with a sealing device having ageneral radial lip structure.

SUMMARY OF THE INVENTION Problem to be Solved by the Invention

However, further functional improvement has been requested with regardto the following points in the sealing device 101 shown in FIG. 13.

More specifically, in the sealing device 101, since the slinger 111rotating together with the rotating shaft 61 exerts a fluid shake-offaction caused by the flange portion 113 and a fluid pumping actioncaused by the thread groove 114 when the rotating shaft 61 rotates, itis possible to suppress leakage of the sealed fluid. However, since acentrifugal force disappears when the rotation of the rotating shaft 61stops, there is a risk that the sealed fluid passes through a leadingend of the seal lip 124 along the thread groove 114 and leaks to themachine outer side B (a so-called risk that a static leakage isgenerated). The static leakage particularly tends to be generated in thecase that an incline is generated in a vehicle body, for example, whenthe motor vehicle stops in the middle of a sloping road, and an oilamount (an oil surface level) within the shaft hole 52 of the enginegoes beyond a lower end of the rotating shaft 61.

The present invention is made by taking the above problems intoconsideration, and an object of the present invention is to provide asealing device having a seal flange and a seal lip which slidably comesinto contact with the seal flange, wherein the sealing device caninhibit the static leakage from being generated when the rotation of therotating shaft stops.

Means for Solving the Problem

The present invention employs the following means for exerting the aboveobject.

A sealing device according to the present invention is a sealing devicesealing so as to prevent a sealed fluid in a machine inner side fromleaking to a machine outer side between a housing and a rotating shaftwhich is inserted to a shaft hole provided in the housing, the sealingdevice comprising: a seal flange which is installed to an outerperiphery of the rotating shaft; a seal lip which is installed to aninner periphery of the shaft hole of the housing; and the seal lipslidably coming into contact with the seal flange over an entireperiphery, wherein the sealing device comprises: a thread groove whichexerts a fluid pumping action when the rotating shaft rotates, andwherein the thread groove is provided at a position which does notintersect a contact area where the seal lip slidably comes into contactwith the seal flange over the entire periphery.

According to the sealing device of the present invention, since thethread groove exerting the fluid pumping action when the rotating shaftrotates is provided at the position which does not intersect the contactarea where the seal lip slidably comes into contact with the seal flangeover the entire periphery, the thread groove does not form a leakageflow path of a static leakage when the rotating shaft stops. Therefore,it is possible to inhibit the static leakage from being generatedthrough the thread groove.

In the present invention, with regard to the position where the threadgroove is provided, and the other structures for enhancing a sealingfunction, the following aspects can be thought.

First Aspect

A thread groove forming area is provided in a machine outer side endface of the seal flange by setting up the thread groove in a part of themachine outer side end face of the seal flange, and a thread groovenon-forming area which is not provided with the thread groove isprovided in an outer peripheral side of the thread groove forming area,thereby slidably bringing the seal lip into contact with the threadgroove non-forming area. Further, an annular projection is provided inan inner peripheral side of the seal lip toward the seal flange, and amicro gap is provided between the projection and the seal flange.

According to the sealing device of the aspect mentioned above, thethread groove non-forming area is provided in the outer peripheral sideof the thread groove forming area in the machine outer side end face ofthe seal flange, and the seal lip comes into contact with the threadgroove non-forming area in the outer peripheral side in place of thethread groove forming area. As a result, a lip end of the seal lip andthe thread groove do not intersect each other. Therefore, the threadgroove does not form the leakage flow path of the static leakage and itis accordingly possible to inhibit the static leakage from beinggenerated through the thread groove.

Further, when the rotating shaft rotates, in addition to a sealingaction exerted by the seal lip, the seal flange exerts a fluid shake-offaction in conjunction with rotation, the thread groove exerts a fluidpumping action in conjunction with rotation, and the micro gap furtherexerts a non-contact labyrinth sealing action. Therefore, it is possibleto inhibit the sealed fluid from leaking to the machine outer side onthe basis of each of the actions.

Further, in the sealing device according to the first aspect mentionedabove, the projection may be structured such that a micro gap is formedbetween the projection and the thread groove forming area in the machineouter side end face of the seal flange.

According to the structure, since the micro gap is formed between theprojection and the thread groove forming area in the machine outer sideend face of the seal flange, the thread groove exerts the fluid pumpingaction according to the rotation in the inner portion of the micro gap,and fluid pumping action covers the entire micro gap width since themicro gap is narrow. Therefore, the sealed fluid passing through theseal lip sliding portion leaks to the machine outer side only afterpassing through the micro gap, however, the pumping action isnecessarily applied to the sealed fluid entering into the micro gap. Asa result, the sealed fluid is hard to pass through the micro gap and isaccordingly hard to leak to the machine outer side. On the basis of theaction mentioned above, the narrower the micro gap width, the better themicro gap function is.

Second Aspect

A thread groove forming area is provided in a machine outer side endface of the seal flange by setting up the thread groove in a part of themachine outer side end face of the seal flange, and a thread groovenon-forming area which is not provided with the thread groove isprovided in the other portion in a machine outer side end face of a sealflange, thereby slidably bringing the partial seal lip among a pluralityof seal lips into contact with the thread groove forming area, andslidably bringing the other seal lip into contact with the thread groovenon-forming area.

According to the sealing device of the aspect mentioned above, anexcellent sealing performance can be exerted by a thread pumping effectobtained by the thread groove extending in a centripetal direction inrelation to a rotating direction, in a sliding portion between thepartial seal lip among a plurality of seal lips and the seal flange,when the rotating shaft rotates, and an excellent sealing performancecan be maintained by the other seal lip which is brought into closecontact with the thread groove non-forming area in the seal flange, whenthe rotating shaft stops.

Further, in the sealing device according to the second aspect mentionedabove, the other seal lip slidably brought into close contact with thethread groove non-forming area may be formed to repel in a lower levelthan the partial seal lip slidably brought into close contact with thethread groove forming area.

According to the structure, it is possible to inhibit friction caused bya sliding motion with the seal flange at a time of rotating from beingincreased.

Third Aspect

In this aspect, the shaft hole and the rotating shaft are structuredsuch that their central axes are set toward a horizontal direction.Further, the sealed fluid may be structured such as to be filled to apredetermined height position within the shaft hole when the rotation ofthe rotating shaft stops. The thread groove is provided on a facingsurface of the seal lip which faces to the machine outer side end faceof the seal flange, and the thread groove is provided only at a positionwhich is above the predetermined height position to which the sealedfluid is filled within the shaft hole when the rotation of the rotatingshaft stops, on the facing surface of the seal lip.

According to the sealing device of the aspect mentioned above, thethread groove exerting the fluid pumping action when the rotating shaftrotates is provided on the facing surface of the seal lip which faces tothe machine outer side end face of the seal flange, and the threadgroove is provided only at the position which is above the predeterminedheight position to which the sealed fluid is filled within the shafthole when the rotation of the rotating shaft stops, on the facingsurface of the seal lip. As a result, the thread groove is not providedat a position which is below the predetermined height position.Therefore, there is not generated a state in which the circumferentiallypartial thread groove 114 is arranged below the liquid surface waterlevel H and is immersed by the sealed fluid, which occurs in the sealingdevice 101 according to the prior art in FIG. 13. Accordingly, it ispossible to effectively suppress generation of the static leakage.

Further, since the thread groove is provided in the seal lip in astationary side (a non-rotating side) in place of the rotating side, itis possible to effectively suppress the generation of the staticleakage.

In the sealing device 101 according to the prior art in FIG. 13, sincethe thread groove 114 is provided in the flange portion 113 of theslinger 111 in the rotating side, it is impossible to previously specifywhat position the thread groove 114 circumferentially stops when therotation stops. As a result, there is left a possibility of generationof the state in which the circumferentially partial thread groove 114 isarranged below the liquid surface water level H and is immersed by thesealed fluid. On the other hand, in the sealing device according to theaspect mentioned above, the thread groove is provided in the seal lip inthe stationary side (the non-rotating side) in place of the rotatingside, thereby doing away with the possibility of generation of the statein which the circumferentially partial thread groove 114 is arrangedbelow the liquid surface water level H and is immersed by the sealedfluid. This structure can be exerted by always fixing thecircumferential position of the thread groove.

Further, in the sealing device according to the third aspect mentionedabove, the predetermined height position at which the sealed fluid isfilled within the shaft hole when the rotation of the rotating shaftstops may be the same or approximately the same as the height positionof the center axis of the rotating shaft. In this case, the threadgroove is provided only circumferentially in an upper half of the facingsurface of the seal lip.

According to the structure, since the thread groove is not provided in alower half area in the facing surface of the seal lip, it is possible tosuppress generation of the static leakage in the lower half area.

Fourth Aspect

A circumferential sealing surface and thread projections are formed on afacing surface to the seal flange in the seal lip, and a thread grooveis formed between the thread projections which are adjacent to eachother in a circumferential direction, the circumferential sealingsurface being capable of coming into close contact with the seal flangein its entire periphery in an outer diameter end portion, and the threadprojections extending in a centripetal direction in relation to anopposite direction to the rotation of the seal flange in an innerdiameter side of the circumferential sealing surface.

According to the sealing device of the aspect mentioned above, since thethread projections formed in the seal lip bring about a thread pumpingaction feeding the fluid existing in the thread groove between thethread projections which are adjacent to each other in thecircumferential direction to the circumferential sealing surface in theouter diameter side on the basis of the rotation of the seal flange, itis possible to secure an excellent sealing performance. Further, since adynamic pressure generated by the thread pumping action acts so as toopen a portion between the circumferential sealing surface and the sealflange from an inner diameter side, a sliding surface pressure isreduced. As a result, a sliding torque of the sliding portion can bereduced. Further, in a state in which the seal flange stops, the dynamicpressure exerted by the thread pumping action is lost, and thecircumferential sealing surface comes into close contact in its entireperiphery with the seal flange. As a result, it is possible toeffectively prevent the leakage at a time of stopping.

Further, in the sealing device according to the fourth aspect mentionedabove, a width of a relative groove portion between the threadprojections which are adjacent in the circumferential direction may benarrowed toward an outer diameter side.

According to the structure, since the width of the groove portion isnarrowed in the course of the fluid existing in the relative groovebetween the thread projections which are adjacent to each other in thecircumferential direction being fed to the outer diameter side on thebasis of the thread pumping action, it is possible to obtain a furtherremarkable dynamic pressure.

Effect of the Invention

According to the present invention, in the sealing device having theseal flange and the seal lip which slidably comes into contact with theseal flange, it is possible to inhibit the static leakage from beinggenerated when the rotation of the rotating shaft stops.

BRIEF EXPLANATION OF THE DRAWINGS

FIG. 1 is a cross sectional view of a substantial part of a sealingdevice according to a first embodiment of the present invention;

FIG. 2 is an explanatory view of a thread groove which is provided inthe sealing device;

FIG. 3 is a cross sectional view of a substantial part of a sealingdevice according to a second embodiment of the present invention;

FIG. 4 is an explanatory view of a thread groove which is provided inthe sealing device;

FIG. 5 is a cross sectional view of a substantial part of a sealingdevice according to a third embodiment of the present invention;

FIG. 6 is an explanatory view of a thread groove which is provided inthe sealing device;

FIG. 7 is an explanatory view of a thread groove according to acomparative example;

FIG. 8 is a cross sectional view of a substantial part of a sealingdevice according to a fourth embodiment of the present invention;

FIG. 9 is an enlarged cross sectional view of a substantial part in FIG.8;

FIG. 10 is a view of an example of a shape of a thread projection asseen from a direction which is parallel to an axis;

FIG. 11 is a view of the other example of the shape of the threadprojection as seen from a direction which is parallel to an axis;

FIG. 12 is a view of the other example of the shape of the threadprojection as seen from a direction which is parallel to an axis; and

FIGS. 13A and 13B are views showing a conventional example, in whichFIG. 13A is a cross sectional view of a substantial part of a sealingdevice according to the conventional example, and FIG. 13B is anexplanatory view of a thread groove which is provided in the sealingdevice.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

Next, a description will be given of embodiments according to thepresent invention with reference to the accompanying drawings.

First Embodiment

FIG. 1 shows a cross section of a substantial part of a sealing device 1according to a first embodiment of the present invention.

The sealing device 1 according to the embodiment is a sealing device (anoil seal for an engine) 1 sealing so as to prevent a sealed fluid (anoil) in a machine inner side (an oil side) A from leaking to a machineouter side (an atmospheric side) B between a housing (a seal housing) 51and a rotating shaft 61 passing through a shaft hole 52 which isprovided in the housing 51, and is constructed by combination of aslinger 11 which is installed to an outer periphery of a rotating shaft61, and a lip seal member 21 which is installed to an inner periphery ofthe shaft hole 52 of the housing 51.

The slinger 11 is made of a rigid material such as metal, integrally hasa sleeve portion 12 which is fixed (fitted) to an outer peripheralsurface of the rotating shaft 61, and a flange portion (a seal flange)13 which is provided in one end (a machine inner side end portion) ofthe sleeve portion 12, is provided in a machine outer side end face 13 aof the flange portion 13 with an annular thread groove forming area 14,and is provided in the thread groove forming area 14 with a threadgroove 15 which exerts an action of pushing back a sealed fluid towardan outer peripheral side (the machine inner side A) by exerting a fluidpumping action caused by a centrifugal force when the rotating shaft 61rotates, as shown in FIG. 2. An arrow e denotes a rotating direction ofthe rotating shaft 61. The thread groove 15 in FIG. 2 is shown as afour-threaded screw.

Further, an annular thread groove non-forming area 16 where any threadgroove is not formed is provided in an outer peripheral side of thethread groove forming area 14 in the machine outer side end face 13 a ofthe flange portion 13 in the same manner. The thread groove non-formingarea 16 is provided as a flat surface which is axially vertical sincethe thread groove is not formed.

In FIG. 1, the thread groove forming area 14 is set in a range shown byE1, and the thread groove non-forming area 16 is set in a range shown byE2.

Meanwhile, the lip seal member 21 has an attachment ring 22 which isfixed (fitted) to an inner peripheral surface of the shaft hole 52 ofthe housing 51 and is made of a rigid material such as metal, and arubber-like elastic body 23 which is attached (adhered in a crosslinkingmanner) to the attachment ring 22, is integrally provided with a seallip (an end face lip) 24 which slidably comes into close contact withthe thread groove non-forming area 16 of the machine outer side end face13 a of the flange portion 13 in the slinger 11, and an annularprojection 25 by the rubber-like elastic body 23, and is structured suchthat a dust lip 26 slidably coming into close contact with an outerperipheral surface of the sleeve portion 12 in the slinger 11 isassembled in the rubber-like elastic body 23.

The projection 25 is provided in an inner peripheral side of the seallip 24, is provided so as to be directed to the flange portion 13 in theslinger 11 from its base end toward a leading end, and forms an annularmicro gap c having a predetermined width (a width in an axial direction)w between the projection 25 and the flange portion 13.

Further, since the projection 25 is provided so as to be directed to thethread groove forming area 14 of the machine outer side end face 13 a ofthe flange portion 13 in the slinger 11, the annular micro gap c havingthe predetermined width (the width in the axial direction) w is formedbetween the projection 25 and the thread groove forming area 14.

Further, since the projection 25 is provided with a leading end face 25a which is formed into an axially perpendicular flat surface, the microgap c has the predetermined width (the width in the axial direction) w,and also has a length (a length in an axially perpendicular direction (adiametrical direction)) L which is greater than the width w.

Further, the projection 25 has the leading end face 25 a which is formedinto the axially perpendicular flat surface, and also has an outerperipheral surface 25 b and an inner peripheral surface 25 c which areformed into a taper surface shape which is inclined in a directionenlarging little by little from a base end toward a leading end.Therefore, the projection 25 is formed as a whole into a parallelogramin a cross section.

In the sealing device 1 having the structure mentioned above, the threadgroove non-forming area 16 is provided in the outer peripheral side ofthe thread groove forming area 14 of the machine outer side end face 13a of the flange portion 13 in the slinger 11, and the seal lip 24 comesinto contact with the latter thread groove non-forming area 16 in placeof the former thread groove forming area 14. As a result, the lip end 24a of the seal lip 24 and the thread groove 15 do not intersect eachother. Therefore, since the thread groove 15 does not form a leakageflow path of the static leakage, it is possible to inhibit the staticleakage from being generated through the thread groove 15.

Further, when the rotating shaft 61 rotates, the sealing action can beexerted by the sliding motion of the seal lip 24 in relation to thethread groove non-forming area 16, the flange portion 13 exerts a fluidshake-off action in conjunction with the rotation, the thread groove 15exerts a fluid pumping action in conjunction with the rotation, and themicro gap c exerts a non-contact type labyrinth sealing action.Therefore, it is possible to inhibit the sealed fluid from leaking tothe machine outer side B on the basis of each of the actions.

Further, in addition, since the projection 25 forms the micro gap cbetween the projection 25 and the thread groove forming area 14 in themachine outer side end face 13 a of the flange portion 13 in the sealingdevice 1 having the structure mentioned above, the thread groove 15exerts the fluid pumping action in conjunction with the rotation in theinner portion of the micro gap c, and the fluid pumping action covers anentire width w thereof since the width w of the micro gap c is narrow.Accordingly, since the sealed fluid leaking through the lip end slidingportion of the seal lip 24 can leak to the machine outer side B onlyafter passing through the micro gap c, and the fluid pumping actionnecessarily covers the sealed fluid entering into the micro gap c, thesealed fluid is hard to pass through the micro gap c and can hardly passthrough the micro gap c. As a result, it is possible to almostcompletely inhibit the sealed fluid leaking through the seal lip 24 frompassing through the micro gap c and leaking to the machine outer side B.

As mentioned above, according to the sealing device 1 of the embodiment,it is possible to achieve an excellent sealing performance in relationto the sealed fluid.

Second Embodiment

In FIG. 3, reference numeral 51 denotes a non-rotating housing, andreference numeral 61 denotes a rotating shaft which is inserted to ashaft hole of the housing 51. A sealing device arranged between thehousing 51 and the rotating shaft 61 is provided with a lip seal member21 which is installed to the housing 51, and a slinger 11 which isinstalled to the rotating shaft 61, and is structured such as to preventan oil to be sealed existing in a machine internal space A in a rightside in FIG. 3 from leaking to a machine external space B in FIG. 3 froman inner periphery of the housing 51.

The lip seal member 21 is constructed by an attachment ring 22 which isfitted and attached by pressure insertion into an inner peripheralsurface of the housing 51, and an inner peripheral side seal lip 27, anouter peripheral side seal lip 28, a gasket portion 29, a dust lip 30and an elastic layer 31 which are integrally formed in the attachmentring 22 by a rubber-like elastic material (a rubber material or asynthetic resin material having a rubber-like elasticity).

The attachment ring 22 and the slinger 11 in the lip seal member 21 aremanufactured by press molding a metal plate such as a steel plate, andthe attachment ring 22 among them is constructed by an outer peripheralfitting portion 22 a which is fitted by pressure insertion into an innerperipheral surface 51 a of the housing 51, a gasket support portion 22 bwhich is formed into a conical tube reducing its diameter toward anopposite side to a machine internal space A from the outer peripheralfitting portion 22 a, a diametrical portion 22 c which extends to aninner diameter side from the gasket support portion 22 b, a conical tubeportion 22 d which extends to the machine internal space A side from aninner diameter end portion of the diametrical portion 22 c so as toreduce its diameter little by little, and a flange portion 22 e whichextends to an inner diameter side from an end portion of the conicaltube portion 22 d. Further, the slinger 11 is constructed by a sleeveportion 12 which is close fitted to an outer peripheral surface of therotating shaft 61 and extends from one end of the sleeve portion 12.

The inner peripheral side seal lip 27 and the outer peripheral side seallip 28 in the lip seal member 21 extend to the machine internal space Aside while forming a conical tube shape each of which is formed so thata leading end is directed to an outer peripheral side from a base whichis an inner diameter portion of an elastic layer 31 positioned in aninner diameter end of the flange portion 22 e in the attachment ring 22,and the leading end portion is slidably brought into close contact withan end face which faces to an opposite side to the machine internalspace A in the seal flange 13 and is formed into a flat surfaceapproximately orthogonal to an axis O. Further, a repulsive force (asurface pressure against the seal flange 13) of the outer peripheralside seal lip 28 generated by being pressed to the seal flange 13 islower than a repulsive force of the inner peripheral side seal lip 27.In the embodiment, the inner peripheral side seal lip 27 corresponds to“partial seal lip” described in claim 3, and the outer peripheral sideseal lip 28 corresponds to “other seal lip”.

A thread groove 15 is formed in a halfway portion in a diametricaldirection in the end face of the seal flange 13 of the slinger 11, andthe thread groove 15 extends in a centripetal direction in relation to ashaft rotating direction (a counterclockwise direction in FIG. 4) asshown in FIG. 4. Further, the leading end portion of the innerperipheral side seal lip 27 in the lip seal member 21 is brought intoclose contact with a forming area (a thread groove forming area) 14 ofthe thread groove 15 in the end face, and the leading end portion of theouter peripheral side seal lip 28 is brought into close contact with athread groove non-forming area 16 closer to an outer diameter side thanthe thread groove forming area 14 in the end face.

The gasket portion 29 in the lip seal member 21 is formed in an outerdiameter end of the elastic layer 31, is positioned in an outerperiphery of the gasket support portion 22 b in the attachment ring 22,and retains an airtightness between the gasket portion 29 and thehousing 51 by being interposed between the gasket support portion 22 band the inner peripheral surface 51 a of the housing 51 with apredetermined collapsing margin.

The dust lip 30 in the lip seal member 21 extends from an inner diameterend of the elastic layer 31 to the machine external space B side whileforming a conical tube, and a leading end portion thereof is close toand faced to an outer peripheral surface of the rotating shaft 61.

In the sealing device structured as mentioned above, the lip seal member21 is fitted and attached by pressure insertion into the innerperipheral surface 51 a of the housing 51 in the outer peripheralfitting portion 22 a of the attachment ring 22, and is close fitted inthe gasket portion 29 with an appropriate collapsing margin, and theinner peripheral side seal lip 27 and the outer peripheral side seal lip28 of the lip seal member 21 come into close contact and slide with theend face of the seal flange 13 of the slinger 11 which integrallyrotates together with the rotating shaft 61, as shown in FIG. 3, therebyinhibiting the oil to be sealed which exists in the machine internalspace A side from leaking to the machine external space B side.

Particularly when the rotating shaft 61 rotates, the seal flange 13 ofthe slinger 11 has an action of shaking the fluid coming into contactwith the seal flange 13 in an outer diameter direction on the basis of acentrifugal force, and the thread groove 15 brings about a threadpumping action feeding out the fluid to the outer diameter side on thebasis of the rotation in the sliding portion between the innerperipheral side seal lip 27 and the seal flange 13 even if a part of theoil to be sealed which exists in the machine internal space A side isgoing to further pass through the sliding portion between the innerperipheral side seal lip 27 and the seal flange 13 to the inner diameterside from the sliding portion between the outer peripheral side seal lip28 and the seal flange 13. As a result, an excellent sealing functioncan be exerted. Further, since the outer peripheral side seal lip 28 islower repulsive than the inner peripheral side seal lip 27, an increaseof friction can be suppressed by the provision of the outer peripheralside seal lip 28.

Further, since an internal pressure in an annular space C definedbetween the inner peripheral side seal lip 27 and the outer peripheralside seal lip 28 is raised by the thread pumping action mentioned above,the sealing performance in the sliding portion between the outerperipheral side seal lip 28 and the seal flange 13 is improved.

Further, in the case that the rotation of the rotating shaft 61 stops,the shake-off action generated by the seal flange 13 of the slinger 11and the thread pumping action of the thread groove 15 are lost, however,since the leading end portion of the outer peripheral side seal lip 28is brought into close contact with the thread groove non-forming area 16which is closer to the outer diameter side than the forming area 14 ofthe thread groove 15 in the end face of the seal flange 13, the leakagepath is not formed by the thread groove 15. Therefore, the excellentsealing performance can be maintained even when the rotating shaft 6stops, or even under a condition that the oil to be sealed exists in themachine internal space A.

In the embodiment mentioned above, the leading end portion of the innerperipheral side seal lip 27 is brought into close contact with theforming area 14 of the thread groove 15, and the leading end portion ofthe outer peripheral side seal lip 28 is brought into close contact withthe thread groove non-forming area 16, however, contrary to this, theleading end of the outer peripheral side seal lip 28 may be brought intoclose contact with the thread groove forming area, and the leading endportion of the inner peripheral side seal lip 27 may be brought intoclose contact with the thread groove non-forming area which is closer tothe inner diameter side than the thread groove forming area.

Further, the present invention can be applied to the structure havingthree or more seal lips.

Third Embodiment

FIG. 5 shows a cross section of a substantial part of a sealing device 1according to a third embodiment of the present invention.

The sealing device 1 according to the embodiment is a sealing device (anoil seal for an engine) 1 sealing so as to prevent a sealed fluid (anoil) in a machine inner side (an oil side) A from leaking to a machineouter side (an atmospheric side) B between a housing (a seal housing) 51and a rotating shaft 61 which is inserted to a shaft hole 52 provided inthe housing 51. As illustrated, the shaft hole 52 and the rotating shaft61 are set so that their center axis O is directed to a horizontaldirection. Further, it is assumed that when the rotation of the rotatingshaft 61 stops, the sealed fluid is filled to a predetermined heightposition within the shaft hole 52, more specifically filled to a heightposition which is equal to or approximately equal to a height positionof the center axis O of the rotating shaft 61. In the drawing, a liquidsurface water level at this time is denoted by reference symbol H.

The sealing device 1 is constructed by a combination of a slinger 11which is installed to an outer periphery of the rotating shaft 61, and alip seal member 21 which is installed to an inner periphery of the shafthole 52 of the housing 51.

The slinger 11 is made of a rigid material such as metal, and integrallyhas a sleeve portion 12 which is fixed (fitted) to an outer peripheralsurface of the rotating shaft 61, and a flange portion (a seal flange)13 which is provided in one end (a machine inner side end portion) ofthe sleeve portion 12. Any thread groove is not provided in a machineouter side end face 13 a of the flange portion 13, and the machine outerside end face 13 a of the flange portion 13 is accordingly formed into asmooth surface.

Meanwhile, the lip seal member 21 has an attachment ring 22 which isfixed (fitted) to an inner peripheral surface of the shaft hole 52 ofthe housing 51 and is made of a rigid material such as metal, and arubber-like elastic body 23 which is attached (adhered in a crosslinkingmanner) to the attachment ring 22, and is integrally provided with aseal lip (an end face lip) 24 which slidably comes into close contactwith the machine outer side end face 13 a of the flange portion 13 inthe slinger 11, an oil recovery lip 32 which does not come into contactwith the slinger 11, and a dust lip 26 which slidably comes into closecontact with an outer peripheral surface of the sleeve portion 12 in theslinger 11, by the rubber-like elastic body 23. The oil recovery lip 32is arranged in a machine outer side B of the seal lip 24, and the dustlip 26 is arranged further in the machine outer side B of the oilrecovery lip 32.

A facing surface 24 b of the seal lip 24 facing to the machine outerside end face 13 a of the flange portion 13 is provided with a threadgroove 33 which exerts an action of pushing back the sealed fluid towardan outer peripheral side (a machine inner side A) by exerting a pumpingaction caused by a centrifugal force when the rotating shaft 61 rotates.Since the seal lip 24 is formed into a tapered (funnel-like) side lipwhich is enlarged its diameter little by little from a base end portionto a leading end portion, the thread groove 33 is provided in an innerperipheral surface of the seal lip 24.

Further, the thread groove 33 is provided only at a position which isabove a predetermined height position where the sealed fluid is filledwithin the shaft hole 52 when the rotation of the rotating shaft 61stops, in the facing surface 24 b of the seal lip 24, as shown in FIG.6, and the sealed fluid is filled in the embodiment to the heightposition which is equal to or approximately equal to the height positionof the center axis O of the rotating shaft 61 as mentioned above.Therefore, the thread groove 33 is provided only in an upper half regionamong the facing surface 24 b of the seal lip 24.

More specifically, if the thread groove 33 is provided over an entireperiphery 360 degrees as shown in FIG. 7 showing a comparative example,the thread groove 33 is arranged below the liquid surface water level Hin a circumferentially lower half region and is in a state in which thethread groove 33 is immersed into the sealed fluid. As a result, thesealed fluid tends to enter into the inner peripheral side of the seallip 24 from the outer peripheral side of the seal lip 24 via the threadgroove 33 in the circumferentially lower half region. On the contrary,in the embodiment, since the thread groove 33 is provided only in thecircumferentially upper half region and is not provided in the lowerhalf region as shown in FIG. 6, the thread groove 33 is structured suchas to be prevented from being arranged below the liquid surface waterlevel H and being immersed into the sealed fluid.

In FIGS. 6 and 7, an arrow e denotes a rotating direction of therotating shaft 61. The thread groove 33 is shown as a four-threadedscrew in FIG. 6.

In the sealing device 1 having the structure mentioned above, the basicsealing function can be exerted by the seal lip 24 slidably coming intoclose contact with the flange portion 13 of the slinger 11 when therotating shaft 61 rotates, the slinger 11 rotating together with therotating shaft 61 exerts the fluid shake-off action caused by the flangeportion 13, and the thread groove 33 provided in the seal lip 24 furtherexerts the fluid pumping action in conjunction with the relativerotation to the flange portion 13. As a result, it is possible to returnthe fluid to the outer peripheral side (the machine inner side A) evenif the fluid passes through between the seal lip 24 and the flangeportion 13, whereby an excellent sealing function can be exerted.

Further, when the rotation of the rotating shaft 61 stops, thecentrifugal force disappears, and the fluid shake-off action and thefluid pumping action temporarily stop in conjunction with thedisappearance. Accordingly, there is fear that the partial sealed fluidflows out to a space D between the seal lip 24 and the oil recovery lip32 from the machine inner side A through the thread groove 33. However,in the present embodiment, since the thread groove 33 is provided onlyat the position which is above the predetermined height position wherethe sealed fluid is filled within the shaft hole 52 when the rotation ofthe rotating shaft 61 stops in the facing surface 24 b of the seal lip24 as mentioned above, there is not generated a state in which thecircumferential partial thread groove 33 is arranged below the liquidsurface water level H and is immersed into the sealed fluid. Therefore,it is possible to suppress the static leakage of the sealed fluid fromthe outer peripheral side of the seal lip 24 to the inner peripheralside through the thread groove 33.

The predetermined height position where the sealed fluid is filledwithin the shaft hole 52 when the rotation of the rotating shaft 61stops is set to the height position which is equal to or approximatelyequal to the height position of the center axis O of the rotating shaft61 as mentioned above as a specific example, however, is not limited tothis in the present invention, but can be set, for example, to a heightposition which is equal to or approximately equal to a height positionof a lower end portion of the rotating shaft 61, as the other example.The lower end portion of the rotating shaft 61 is here acircumferentially lower end portion on the outer peripheral surface ofthe rotating shaft 61 which is set by directing the center axis O to thehorizontal direction. Further, in this case, since a region which formsthe thread groove 33 is increased and a region which does not form thethread groove 33 is decreased in the facing surface 24 b of the seal lip24 in comparison with the embodiment mentioned above, it is possible toenhance the fluid pumping action generated by the thread groove 33.

Fourth Embodiment

In FIG. 8, reference numeral 51 denotes a non-rotating housing, andreference numeral 61 denotes a rotating shaft which is inserted to ashaft hole of the housing 51. A sealing device arranged between thehousing 51 and the rotating shaft 61 has an end face lip type sealstructure, is provided with a lip seal member 21 which is installed tothe housing 51, and a slinger 11 which is installed to the rotatingshaft 61, and is structured such as to prevent a sealed fluid (an oil)existing in a machine internal space A in a right side in FIG. 8 fromleaking to a machine external space B in FIG. 8 from an inner peripheryof the housing 51.

The lip seal member 21 is constructed by an attachment ring 22 which isfitted and attached by pressure insertion into an inner peripheralsurface of the housing 51, and a seal lip 24, a gasket portion 29, adust lip 30 and an elastic layer 31 which are integrally formed in theattachment ring 22 by a rubber-like elastic material (a rubber materialor a synthetic resin material having a rubber-like elasticity).

The attachment ring 22 in the lip seal member 21, and the slinger 11 aremanufactured by press molding a metal plate such as a steel plate, andthe attachment ring 22 among them is constructed by an outer peripheralfitting portion 22 a which is fitted by pressure insertion into an innerperipheral surface 51 a of the housing 51, a gasket support portion 22 bwhich is formed into a conical tube reducing its diameter toward anopposite side to a machine internal space A from the outer peripheralfitting portion 22 a, a diametrical portion 22 c which extends to aninner diameter side from the gasket support portion 22 b, a conical tubeportion 22 d which extends to the machine internal space A side from aninner diameter end portion of the diametrical portion 22 c so as toreduce its diameter little by little, and a flange portion 22 e whichextends to an inner diameter side from an end portion of the conicaltube portion 22 d. Further, the slinger 11 is constructed by a sleeveportion 12 which is close fitted to an outer peripheral surface of therotating shaft 61 and the seal flange 13 which extends from one end ofthe sleeve portion 12.

The seal lip 24 in the lip seal member 21 is extending to the machineinternal space A side while forming a conical tube shape which is formedso that a leading end is directed to an outer peripheral side from abase which is an inner diameter portion of an elastic layer 31positioned in an inner diameter end of the flange portion 22 e in theattachment ring 22.

An outer diameter end portion of the facing surface to the seal flange13 in the seal lip 24 is formed into a circumferential sealing surface24 c which is formed flat in its entire periphery and can come intoclose contact with the seal flange 13, as shown in FIGS. 9 and 10, and alot of thread projections 34 are formed uniformly in a circumferentialdirection in an inner diameter side of the circumferential sealingsurface 24 c.

Each of the thread projections 34 extends in a centripetal direction inrelation to an opposite direction (a counterclockwise direction in FIG.10) to the rotation of the seal flange 13, reaches the circumferentialsealing surface 24 c in its outer diameter end portion 34 a, and bringsabout a thread pumping action of feeding the fluid existing in therelative thread groove 35 between the circumferentially adjoin threadprojections 34 and 34 to the circumferential sealing surface 24 c whenthe seal flange 13 rotates in a clockwise direction in FIG. 10. Further,the thread projection 34 is formed into a bulge shape in which a topportion 34 c is unevenly distributed in an inner diameter end portion 34b side, and is formed at a bulge height which does not prevent closecontact of the circumferential sealing surface 24 c with the seal flange13.

Turning the description back to FIG. 8, the gasket portion 29 in the lipseal member 21 is formed in an outer diameter end of the elastic layer31, is positioned in an outer periphery of the gasket support portion 22b in the attachment ring 22, and is interposed between the gasketsupport portion 22 b and the inner peripheral surface 51 a of thehousing 51 with a predetermined collapsing margin, thereby retaining theairtightness between the gasket portion 29 and the housing 51.

The dust lip 30 in the lip seal member 21 extends from an inner diameterend of the elastic layer 31 to the machine external space B side whileforming a conical tube, and comes close to and faces to an outerperipheral surface of the rotating shaft 61 in its leading end portion.Further, a plurality of ribs 30 a are formed at predetermined intervalsin a circumferential direction on an inner peripheral surface of thedust lip 30, the ribs 30 a supporting in a state in which a leading endportion of the dust lip 30 floats slightly up from an outer peripheralsurface of the rotating shaft 61, thereby preventing the innerperipheral space D of the seal lip 24 from becoming negative pressuredue to the shake-off action of the seal flange 13 in the slinger 11 andthe thread pumping action of the thread projection 34 in the seal lip24.

In the sealing device according to the embodiment having the structurementioned above, the lip seal member 21 is close fitted in the gasketportion 29 with the appropriate collapsing margin, as well as beingfitted and attached by pressure insertion into the inner peripheralsurface 51 a of the housing 51 in the outer peripheral fitting portion22 a of the attachment ring 22, and the circumferential sealing surface24 c of the seal lip 24 in the lip seal member 21 comes into slidablecontact with the end face of the seal flange 13 in the slinger 11integrally rotating with the rotating shaft 61, as shown in FIG. 8,thereby inhibiting the sealed fluid (the oil) existing in the machineinternal space A side from leaking to the machine external space B side.

Particularly when the rotating shaft 61 rotates, there is generated thethread pumping action that the fluid (the air) existing in the relativegroove portion (the thread groove) 35 between the circumferentiallyadjacent thread projections 34 and 34 is guided to the outer diameterside by the thread projections 34 so that the fluid is going to flow ina clockwise direction in FIG. 10 so as to be dragged to the seal flange13, in the inner diameter side of the circumferential sealing surface 24c of the seal lip 24 which is brought into close contact with the sealflange 13, in addition to the matter that the seal flange 13 of theslinger 11 rotating integrally with the rotating shaft 61 has the actionof shaking off the fluid coming into contact with the seal flange 13 inthe outer diameter direction on the basis of the centrifugal force. As aresult, the sealed fluid (the oil) existing in the machine internalspace A side can not easily enter into the inner diameter side from theouter diameter side of the circumferential sealing surface 24 c, and anexcellent sealing performance can be exerted.

Further, since a distance in an axial direction between the facingsurfaces of the seal lip 24 and the seal flange 13 is narrowed toward anouter diameter side (a circumferential sealing surface 24 c side), thefluid (the air) existing in the relative groove portion 35 between thecircumferentially adjacent thread projections 34 and 34 is exposed to acompression in an axial direction in the process of being fed to theouter diameter side on the basis of the shake-off action and the threadpumping action mentioned above, and generates a dynamic pressure.Further, the sliding surface pressure is lower in this kind of end facelip type sealing device in which the seal lip 24 is brought intoslidable contact with the seal flange 13 in the axial direction, incomparison with a type that the seal lip is brought into slidablecontact with the outer peripheral surface of the rotating shaft, and thedynamic pressure additionally acts so as to open the portion between thecircumferential sealing surface 24 c of the seal lip 24 and the sealflange 13 from the inner diameter side. Therefore, the sliding surfacepressure is lowered, and a sliding torque is accordingly lowered,thereby contributing to low fuel consumption.

Further, in a state in which the slinger 11 (the seal flange 13) stopsdue to the stop of the rotating shaft 61, the dynamic pressure caused bythe shake-off action and the thread pumping action mentioned above islost, the circumferential sealing surface 24 c comes into close contactwith the seal flange 13 in its entire periphery and the surface pressureof the circumferential sealing surface 24 c is increased. Accordingly,the leakage path is not formed. Therefore, for example, even in the casethat the axis of the rotating shaft 61 is approximately horizontal andthe lower half portions of the seal lip 24 and the seal flange 13 areimmersed into the sealed fluid (the oil) at a time of stopping, it ispossible to effectively prevent the fluid to be sealed from enteringinto the inner diameter side from the outer diameter side of thecircumferential sealing surface 24 c and leaking to the machine externalspace B side.

In an example shown in FIG. 10, a width of the thread projection 34 isapproximately the same in an outer diameter end portion 34 a side and aninner diameter end portion 34 b side, and a relative groove portion 35between the circumferentially adjoin thread projections 34 and 34 isgreater in a width w_(o) in the outer diameter end portion side than ina width w_(i) in the inner diameter end portion side. However, anexample shown in FIG. 11 is structured such that the width w_(i) in theinner diameter end portion side of the relative groove portion 35 is setto be approximately the same as the width w_(o) in the outer diameterend portion side, and an example shown in FIG. 12 is structured suchthat the width w_(o) in the outer diameter end portion side is set to besmaller than the width w_(i) in the inner diameter end portion side ofthe relative groove portion 35. As a result, in both of the exampleshown in FIG. 11 and the example shown in FIG. 12, the thread projection34 is formed into a shape a width of which is increased in the outerdiameter end portion 34 a side than in the inner diameter end portion 34b side.

According to the structure, the dynamic pressure effect acting so as toopen the portion between the circumferential sealing surface 24 c of theseal lip 24 and the seal flange 13 from the inner diameter side at atime of rotating is improved, in comparison with the structure in whichthe width of the relative groove portion 35 between the threadprojections 34 and 34 is enlarged toward the outer diameter end portionside such as the example shown in FIG. 10. Particularly, since thedynamic pressure effect is further improved in the structure in whichthe width of the relative groove portion 35 is narrowed toward the outerdiameter side such as the example shown in FIG. 12, it is possible toachieve a further sliding torque reduction.

The invention claimed is:
 1. A sealing device sealing so as to prevent asealed fluid in a machine inner side from leaking to a machine outerside between a housing and a rotating shaft which is inserted to a shafthole provided in the housing, the sealing device comprising: a sealflange which is installed to an outer periphery of the rotating shaft;and an elastic seal lip which is installed to an inner periphery of theshaft hole of the housing, the elastic seal lip having a conical tubesurface that extends toward the seal flange and the machine inner sidesuch that an outer diameter end of the elastic seal lip is elasticallypressed against the seal flange; wherein the conical tube surfaceincludes an inner diameter end and an outer diameter end, the outerdiameter end of the conical tube surface includes a circumferentialsealing surface in contact with the seal flange having a predeterminedwidth along an entire length thereof, a plurality of discrete threadprojections are provided on the conical tube surface of the elastic seallip that faces the seal flange, the discrete thread projections eachextending in a centripetal direction toward the circumferential sealingsurface without extending into a contact area of the circumferentialsealing surface defined by the predetermined width, the discrete threadprojections are each identical and have a length that is less than adistance between the inner diameter end and the outer diameter end ofthe conical tube surface and that extends in the centripetal directionfrom an edge of the contact area to a position located radially inboardfrom the edge of the contact area, a width, and a greatest height, thegreatest height of each of the discrete thread projections being locateddistal from the edge of the contact area and immediately adjacent theposition located radially inboard from the edge of the contact area, anda plurality of thread grooves formed on the surface of the elastic seallip that faces the seal flange between each of the discrete threadprojections, the thread grooves each exerting a fluid pumping actionwhen the rotating shaft rotates, and each of the thread grooves also notextending into the contact area defined by the circumferential sealingsurface; a width of each of the threaded grooves between the discretethread projections which are adjacent in the circumferential directionis narrowed in a direction toward the outer diameter end of the conicaltube surface; and the width of each of the threaded projections isgreatest at a location proximate the outer diameter end of the conicaltube surface.
 2. The sealing device according to claim 1, wherein thewidth of each of the thread projections is greatest at a locationproximate the edge of the contact area.
 3. The sealing device accordingto claim 1, wherein each of the thread projections includes atriangular-shaped face that faces the edge of the contact area.